CN203384246U - Double-piston disconnecting device for power transmission unit, and corresponding clutch unit - Google Patents
Double-piston disconnecting device for power transmission unit, and corresponding clutch unit Download PDFInfo
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- CN203384246U CN203384246U CN201320229055.0U CN201320229055U CN203384246U CN 203384246 U CN203384246 U CN 203384246U CN 201320229055 U CN201320229055 U CN 201320229055U CN 203384246 U CN203384246 U CN 203384246U
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- Prior art keywords
- piston
- power transmission
- recess
- transmission unit
- cut
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0632—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with conical friction surfaces, e.g. cone clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/0693—Clutches with hydraulic actuation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
- F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
- F16H2063/303—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes the friction member is actuated and released by applying pressure to different fluid chambers
Abstract
A double-piston disconnecting device for a power transmission unit comprises a shell comprising a first concave part and a second concave part, a first piston comprising a first part embedded in the first concave part, a second piston comprising a second part embedded in the second concave part, and an actuator provided with a first side and a second side, wherein the first piston is selectively pressed and leant against the first side of the actuator; the second piston is selectively pressed and leant against the second side of the actuator. A clutch unit comprises the shell, the first piston, the second piston and a synchronizer component.
Description
The cross reference of related application
The application requires the preference of the U.S. Provisional Patent Application 61/678825 of submission on August 2nd, 2012, and its full content is by reference to being incorporated in this specification.
Technical field
The utility model relates generally to piston system.More specifically, the utility model relates to for activating system clutch, that comprise two opposed pistons.
Background technique
Current automotive power transmission system can comprise all-wheel-drive system (" AWD ") system, and wherein all wheels of power transmission system all initiatively participate in propelled vehicles.Some AWD systems have the engine power of reception with the main driving axle for propelled vehicles.Auxiliary drive shaft can participate in from main driving axle receiving part engine power in the active with the whole wheels for power transmission system.Other system can be between main driving axle and auxiliary drive shaft distributed power.
Some AWD vehicles comprise cut off, in order to vehicle is converted to front-wheel drive (" FWD ") or rear wheel drive (" RWD ") by AWD.FWD or RWD system are by the front or rear shaft-driven vehicle of an active.Remaining axle by main driving axle, pulled or promotion until the AWD pattern started.
Cut off comprises clutch and single piston, also comprises in some embodiments reverse shift fork.Thereby clutch can engage engine power is distributed to live axle, thereby and clutch can discharge and stop power transmission to one in live axle.Thereby this single piston can promote clutch engages clutch, thereby reverse shift fork energy release plunger pressure makes clutch separation.The cut off of prior art has the various interface that is connected alternately with housing with for power piston, for example opening and the passage in order to hold reverse shift fork in housing.Therefore, the device of prior art easily leaks, at interface position, is subject to stress and usually bulky.In addition, reverse shift fork easily ruptures.
The model utility content
Double piston type disclosed herein disconnect (cut-outs) device provide a kind of weight gentlier, compactness, energy efficient, the high and durable cut off of cost benefit.
Piston system as the double piston type cut off can comprise housing, and this housing comprises the first recess and the second recess.First piston comprises the first portion be embedded in the first recess.The second piston comprises the second portion be embedded in the second recess.Actuator has the first side and the second side.First piston optionally presses the first side of actuator, and the second piston optionally presses the second side of actuator.
Piston system can form the part of synchronizer assembly, and this synchronizer assembly comprises clutch ring and conical clutch.First piston is configured to optionally make clutch ring separate from conical clutch, and the second piston structure becomes optionally to make clutch ring engage with conical clutch.
Double piston type cut off of the present utility model has following favorable characteristics:
-first piston and the second piston are opposed, and the first side of this actuator is to this first piston, and the second side of this actuator is to this second piston;
-this actuator comprises lip shape section, and this first piston and the second piston are pressed in this lip shape section;
-first piston and the second piston are coaxial;
-this first piston has the external diameter larger than the external diameter of the second piston;
The first side of-described actuator has the first surface area, and the first portion of first piston of optionally pressing the first side of actuator has the surface area less than half surface area of this first surface area;
The second side of-described actuator has the second surface area, and the second portion of the second piston that optionally presses the second side of actuator has the surface area less than half surface area of this second surface area;
-first piston and the second piston all do not rotate;
-actuator is the clutch ring for clutch;
-this housing surrounds this first piston, this second piston and this actuator fully;
-first piston optionally towards or deviate from the second piston and move, the second piston optionally towards or deviate from first piston and move;
-also comprise the hydraulic systems be communicated with first piston and the second piston fluid, wherein, when first piston, when the second piston moves, this second plunger backer moves from this first piston;
-first piston also comprises the first seal ring in the recess in first portion, and the second piston also comprises the second seal ring in the recess in second portion;
-this first piston and this housing, this first seal ring and the seal ring that at least one is other coordinate to form the first square sealing arrangement, and this second piston and this housing, this second seal ring and the seal ring that at least one is other coordinate to form the second square sealing arrangement;
-this housing also comprises: at least one the 3rd recess of contiguous first piston, and the 3rd recess configuration becomes to receive Sealing; And at least one the 4th recess of contiguous the second piston, the 4th recess configuration becomes to receive Sealing;
-first piston also comprises the recess in first portion, and the second piston also comprises the recess in second portion.
The utility model also provides a kind of clutch unit, and this clutch unit comprises: housing, and this housing comprises the first recess and the second recess; First piston, this first piston comprises the first portion be embedded in the first recess; The second piston, this second piston comprises the second portion be embedded in the second recess; And synchronizer assembly, this synchronizer assembly comprises clutch ring and conical clutch, wherein, this first piston is configured to optionally make clutch ring separate from conical clutch, and this second piston structure becomes optionally to make clutch ring engage with conical clutch.
Clutch unit of the present utility model has following favorable characteristics:
-this housing surrounds this first piston, this second piston and this synchronizer assembly fully;
-first piston and the second piston are coaxial, and the external diameter of first piston is greater than the external diameter of the second piston; And
-also comprise the hydraulic systems be communicated with first piston and the second piston fluid, wherein, when first piston, when the second piston moves, this second plunger backer moves from this first piston.
Should be understood that, above-mentioned general description and ensuing detailed description are only all exemplary and explanatory, and do not limit the utility model.
The accompanying drawing explanation
The accompanying drawing that is combined in specification and forms a specification part illustrates instruction of the present utility model.
Fig. 1 is the schematic diagram that the AWD transmission system is converted to FWD.
Fig. 2 is the schematic diagram of double-piston system.
Fig. 3 is the schematic diagram of the double-piston system in power transmission unit.
Fig. 4 is the exploded view of the critical piece of Fig. 3.
Fig. 5 A is the perspective view of the first side of first piston.
Fig. 5 B is the perspective view of the second side of first piston.
Fig. 6 A is the perspective view of the first side of the second piston.
Fig. 6 B is the perspective view of the second side of the second piston.
Fig. 7 is the schematic diagram of the hydraulic control system of piston.
Fig. 8 is the schematic diagram with the electric and hydraulic connecting of housing.
Embodiment
Referring now to the embodiment shown in accompanying drawing, be described in detail, as much as possible, identical reference character all will be used to refer to same or similar parts in accompanying drawing.The mark of directivity, left or right for example, be accompanying drawing but not mean restriction for ease of reference.
Fig. 1 is the example of the power transmission system that can change between AWD and FWD.The element of many routines has been omitted.Motor 103 offers speed changer 102 by torque power.Power transmission unit 101 is connected to drive axle moment of torsion is offered to the front outer output axle shaft 105 and 104 on left side and right side.Power transmission unit 101 also passes through optionally to be connected alternately with small gear 107 (connect by interface, interact) and controls the torque distribution to rear axle, and this small gear 107 connects live axles 112 via joiner 106.The moment of torsion that rear differential mechanism 113 receives from live axle 112, and this moment of torsion is assigned to left and right rear axle 115 and 114.
At least one hydraulic systems 119 is connected to power transmission unit 101 so that actuation force to be provided.Hydraulic systems 119 is connected to electronic control system 120 to control for timing and torque capacity.Electronic control system 120 can be distributed in power transmission system on sensor be connected, for example detect the sensor of small gear 107 rotating speeds, or for the sensor of the speed of wheel speed, rear differential mechanism 113, front axle speed, engine speed, transmission gear selection etc.In some cases, sensor can connect steering column, gas pedal or clutch pedal in order to gather extra data.Information based on being gathered by sensor, the processor in electronic control system 120 can be carried out the program be stored in storage device, and electronic control system 120 can order hydraulic systems 119 that fluid-actuated power is provided.
Fig. 2 illustrates the example of double-piston system.First piston 1 and the second piston 2 move in the opposite direction.Piston 1,2 all is embedded in housing 3, and this housing can be integrated part or split type counterpart.In one embodiment, housing 3 is the two-piece component that match along the plane between opposed piston 1 and 2.Housing 3 has the recess 6,7 for each piston 1,2.Recess 6,7 comprises and being connected of hydraulic systems.For preventing hydraulic flow leakage, housing 3 can have two extra recesses for holding O shape, to enclose 4,5.O shape circle can be square ring (star seal ring, quad ring seal), or the PTFE(teflon) scrape dirty seal ring, it has the ability that chip is scraped off from the hole of recess 6 and 7.In addition, each piston 1,2 can comprise that two respectively in order to hold the recess of O shape circle 8 and 9.These O shape circles can be that square seal ring or PTFE scrape dirty seal ring equally.Perhaps, O shape circle 4 and 8 can be wear ring, and O shape circle 5 and 9 can be square seal ring.Size, number and the interval of the recess on housing 3 or piston 1 and 2 and O shape circle can change.
In the example of Fig. 2, opposed piston 1 and 2 moves to control actuator, is dog formula (pawl type, jack catchs type) clutch ring 10 in this example.Namely, first piston 1 is the isolation piston that clutch ring 10 is slided to the right.The second piston 2 is to press clutch ring 10 so that its joint piston slided left.In this layout, along with first piston 1 moves right, the second piston 2 is moved to the left.When the second piston 2 moves right, first piston 1 is moved to the left, and clutch ring 10 moves with piston 1 and 2.The joint of attached conical clutch 14 in the motion control of clutch ring 10, and this can be the part of " synchromesh ".Although Fig. 2 illustrates an example of synchromesh clutch, dual piston arrangement also can be implemented together with other clutch system with actuator dial slidably.
Fig. 2 illustrates the example by the actuator of two piston actuated.Sectional drawing is to have as the synchronizer mechanisms of torque transmitting mechanisms and the power transmission unit of conical clutch.Actuator can be clutch ring 10, and it slides and be attached thereto and connects on synchronizer input hub 11, and this synchronizer input hub 11 has the synchronizer pillar 12 of distribution.This synchronizer input hub is connected to drive axle by key (keyway), and this drive axle receives rotating power from speed changer.This drive axle can be worked as when torque power is transferred to drive axle and rotates.
The rotating force of drive axle optionally is connected to cone 14 and the microsyn output key ring 13 of conical clutch.Namely, when engaging piston 2 pushing clutch rings 10 and it is pushed away left, clutch ring 10 slides on a cone 14 of outermost.A cone 14 of outermost can rotate and make all the other cones 14 to start rotation.Namely, cone 14 forces together and frictional force impels cone to rotate together with microsyn output key ring 13.The rotation of cone 14 makes microsyn output key ring 13 reach the speed identical with clutch ring 10.The speed of coupling allows the synchronizer pillar 12 on baffle ring (friction ring) or synchronizer input hub 11 to be regulated.Thereby clutch ring 10 can then slide on microsyn output key ring 13 transmission allowed from the moment of torsion of synchronizer input hub 11.
The moment of torsion of front axle can be transmitted smoothly by engaging pressing gradually of piston.This has allowed the level and smooth torque transfer from the main driving axle to the auxiliary drive shaft.
Discharge torque transfer, the first isolation piston 1 optionally moves right so that clutch ring slides off microsyn output key ring 13.Then thereby cone 14 can be separated the transmission that no longer continues moment of torsion.In this example, because the softness of clutch is enough to make its separation, separates and do not need spring.The omission of spring has reduced frictional loss and hysteresis, and has therefore improved fuel economy.
Several benefits have been guaranteed by above-mentioned layout.At first, if power is lost, synchronizer can remain on its current position, has avoided the too early or unexpected disconnection of torque transfer, and the cut of the middle vehicle that travels accordingly.In addition, this system lacks the selector fork of prior art, and this has further reduced the loss that lags behind and bring, because do not exist shift fork to cause connecting the problem of the stirring of fluid.
Replace above-mentioned shortcoming, double- piston 1 and 2 does not rotate and can not increase the hysteresis loss that the spring of prior art or shift fork are arranged.In addition, the piston of array allows stair-stepping configuration with one heart.This allows housing 3 Yan Congqi center vehicle locations to become less to its outer peripheral direction.This has reduced floor space and the weight of power transmission unit 101, and it more easily is assembled near the narrow space such as motor, speed changer.Because piston 1 and 2 is embedded in housing 3, rather than be independent of housing 3, therefore do not need extra support and connection, this has further reduced hysteresis loss and the weight of power transmission unit 101.The minimizing of weight and the minimizing of hysteresis loss have improved the fuel efficiency of vehicle.The minimizing lagged behind also contributes to the idle running more completely of assistant drive system.Namely because power transmission system can be from cone 14 or microsyn output key ring 13 until auxiliary drive shaft can dally, so unlikely rotation or otherwise move or engage of the part that is connected to assistant drive system.In the example of Fig. 2, this means if AWD disconnects and FWD engages, drive axle will receive all torsion torque power and rear axle 115 with 114 will by together with drag.Small gear 107 and live axle 112 will dally, as the hypoid gear of power transmission unit 101.
Existing mode of execution, for example the mode of execution for the idle running assistant drive system is not only used conical clutch but also use the wet clutch group in unsettled U. S. application 12/944714.Current double-piston system can be used in such double clutch system, or as shown here, this double-piston system can be surrounded conical clutch and be cancelled wet clutch, makes conical clutch as unique torque transmitting mechanisms.The cancellation of wet clutch has further reduced weight and hysteresis loss.Piston 1 is connected with the moment of torsion that 2 level and smooth and controlled joint can produce smooth controlled, and dog formula part has been guaranteed fully and firmly engage.
As shown in Figure 2, clutch ring 10 can comprise the outwards outstanding lip shape section of rotation center line that deviates from.Lip shape section provides the surface of pressing for piston 1 and 2.Namely, the first side 20 of isolation piston 1 pushing lip shape section, and engage the second side 21 that piston 2 pushes lip shape sections.Each side 20,21 of lip shape section all has surface area, and piston 1,2 comprises respectively the surface 22,23 with corresponding area of contact.The piston 1 contacted with 21 with lip shape section respective side 20 and 2 area of contact are significantly less than the surface area of lip shape section both sides 20 and 21.In addition, from piston 1, it seems, surface 22 can be greater than area of contact.In addition, the piston face area in contact area can be lip shape section both sides 20,21 surface area half or be less than half.The difference of piston area of contact 22,23 and lip shape section both sides 20,21 surface areas has avoided destroying the excessive power of clutch ring 10.
Referring to Fig. 3, power transmission unit 101 illustrates with another kind of view.Housing comprises two parts 3 and 3 '.The 3rd housing parts can surround part drive axle, half shaft flange 16 and hypoid gear 15.The part that is arranged in power transmission unit of drive axle can be output axle shaft 17.
Fig. 4 illustrates the decomposed figure of Fig. 3.Roller bearing 24 is clamped between half shaft flange 16 and housing parts 3.Other bearing, Sealing and connection are illustrated between output axle shaft 17 and housing parts 3 ' with disconnect mode.Housing parts 3 can be bolted to speed changer 102, or it can be bolted on other housing parts that surrounds hypoid gear 15.
Fig. 5 A is the perspective view of the first side of first piston 1, and Fig. 5 B is the perspective view of the second side of first piston 1.Area of contact and surface 22 are also shown in Fig. 5 A.
Fig. 6 A is the perspective view of the first side of the second piston 2, and Fig. 6 B is the perspective view of the second side of the second piston 2.Area of contact and surface 23 are also shown in Fig. 6 A.
Fig. 7 is the schematic diagram for the hydraulic control system of piston 1 and 2.Hydraulic fluid supply tube 70 is connected on the recess 7 of housing 3 '.Pressure transducer 71 detects whether too much pressure is provided for recess 7, if discharge unnecessary pressure by petcock 72.Supply tube 70 is connected to vacuum pump 73, and this vacuum pump is driven by motor 74.Vacuum pump 73 is connected with supply tube 77, and this supply tube 77 is connected to pressure relief valve 75 and sensor 76 equally.This supply tube is connected to recess 6.By such setting, when fluid is supplied to recess 6, this fluid is taken away from recess 7, or vice versa, thereby keeps piston 1 and 2 synchronous reversing motions.Consider hydraulic fluid loss or pressure relief function in lifetime of system, accumulator 78 or storage tank are connected with each supply tube 70,77.
Pressure transducer 71 with 76 and pressure relief valve 72 and 75 can with electronic control system 120, be connected respectively with for data capture and adjusting.Perhaps, pressure relief valve 72 and 75 predeterminable when being greater than particular value release pressure.Also may need to comprise additional pressure transducer and earth pressure release point and additional electric control device.
The double-piston system can be connected alternately with electronic control system 120 or hydraulic control system 119, electronic control system 120 or hydraulic control system 119 are for example disclosed in common unsettled U. S. application 12/944714, and the full content of this application is by reference to introducing in this specification.Minimally, electronic control system 120 can comprise processor, storage and be stored in the control program be arranged on the storage that plate carries chip or vehicle-mounted computer system.Above-mentioned vehicle sensors can have and being electrically connected to and input and output of electronic control system 102.Electronic control system 102 can have with the electric input and output of hydraulic control system 119 and is connected.
As shown in Figure 8, can be connected with hydraulic actuator 80 81 form with associated electrical and be arranged on housing parts 3 ' for controlling double-piston 1 and at least one hydro-joining of 2.Hydraulic actuator 80 can be held in Fig. 7 whole parts of crossing over recess 6 and 7, or hydraulic actuator can comprise with larger in hydraulic control system 119 or input and output independent hydraulic systems and being connected.
In explanation in front, various instructions are set forth with reference to accompanying drawing.But, it is evident that, in the situation that do not deviate from the relative broad range of claims, can carry out various other variants and modifications to it, and can implement extra configuration.Therefore specification and accompanying drawing are considered to indicative and nonrestrictive.
For example, double-piston is illustrated in front-wheel drive (FWD) system, but it can implement equally in the rear-guard unit of rear wheel drive (RWD) vehicle.Equally, the double-piston design can be applied to disconnecting the transmission situation of transmission system.In addition, the double piston type cut off can be applicable to motor vehicle driven by mixed power.
In the situation that this specification is understood and instruction disclosed herein is put into practice, other embodiment will be apparent to those skilled in the art.Specification and example only are intended to exemplary illustration, and actual range and spirit are indicated by claims.
Claims (20)
1. the cut off of the double piston type for power transmission unit comprises:
Housing, this housing comprises the first recess and the second recess;
First piston, this first piston comprises the first portion be embedded in the first recess;
The second piston, this second piston comprises the second portion be embedded in the second recess; And
Actuator, this actuator has the first side and the second side;
Wherein, this first piston optionally presses the first side of actuator; And
Wherein, this second piston optionally presses the second side of actuator.
2. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, first piston and the second piston are opposed, and the first side of this actuator is to this first piston, and the second side of this actuator is to this second piston.
3. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, this actuator comprises lip shape section, and this first piston and the second piston are pressed in this lip shape section.
4. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, first piston and the second piston are coaxial.
5. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, this first piston has the external diameter larger than the external diameter of the second piston.
6. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, the first side of actuator has the first surface area, and the first portion of first piston of optionally pressing the first side of actuator has the surface area less than half surface area of this first surface area.
7. according to the cut off of the double piston type for power transmission unit of claim 6, wherein, the second side of actuator has the second surface area, and the second portion of the second piston that optionally presses the second side of actuator has the surface area less than half surface area of this second surface area.
8. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, first piston and the second piston all do not rotate.
9. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, actuator is the clutch ring for clutch.
10. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, this housing surrounds this first piston, this second piston and this actuator fully.
11. according to the cut off of the double piston type for power transmission unit of claim 1, wherein, first piston optionally towards or deviate from the second piston and move, the second piston optionally towards or deviate from first piston and move.
12. the cut off of the double piston type for power transmission unit according to claim 11, also comprise the hydraulic systems be communicated with first piston and the second piston fluid, wherein, when first piston, when the second piston moves, this second plunger backer moves from this first piston.
13., according to the cut off of the double piston type for power transmission unit of claim 1, wherein, first piston also comprises the first seal ring in the recess in first portion, the second piston also comprises the second seal ring in the recess in second portion.
14. the cut off of the double piston type for power transmission unit according to claim 13, wherein, this first piston and this housing, this first seal ring and the seal ring that at least one is other coordinate to form the first square sealing arrangement, and this second piston and this housing, this second seal ring and the seal ring that at least one is other coordinate to form the second square sealing arrangement.
15., according to the cut off of the double piston type for power transmission unit of claim 1, wherein, this housing also comprises:
At least one the 3rd recess of contiguous first piston, the 3rd recess configuration becomes to receive Sealing; And
At least one the 4th recess of contiguous the second piston, the 4th recess configuration becomes to receive Sealing.
16., according to the cut off of the double piston type for power transmission unit of claim 1, wherein, first piston also comprises the recess in first portion, the second piston also comprises the recess in second portion.
17. a clutch unit comprises:
Housing, this housing comprises the first recess and the second recess;
First piston, this first piston comprises the first portion be embedded in the first recess;
The second piston, this second piston comprises the second portion be embedded in the second recess; And
Synchronizer assembly, this synchronizer assembly comprises clutch ring and conical clutch,
Wherein, this first piston is configured to optionally make clutch ring separate from conical clutch, and this second piston structure becomes optionally to make clutch ring engage with conical clutch.
18., according to the clutch unit of claim 17, wherein, this housing surrounds this first piston, this second piston and this synchronizer assembly fully.
19., according to the clutch unit of claim 17, wherein, first piston and the second piston are coaxial, the external diameter of first piston is greater than the external diameter of the second piston.
20. according to the clutch unit of claim 17, also comprise the hydraulic systems be communicated with first piston and the second piston fluid, wherein, when first piston, when the second piston moves, this second plunger backer moves from this first piston.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201261678825P | 2012-08-02 | 2012-08-02 | |
| US61/678,825 | 2012-08-02 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203384246U true CN203384246U (en) | 2014-01-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320229055.0U Expired - Lifetime CN203384246U (en) | 2012-08-02 | 2013-03-15 | Double-piston disconnecting device for power transmission unit, and corresponding clutch unit |
| CN201310156198.8A Active CN103573852B (en) | 2012-08-02 | 2013-03-15 | Dual Piston for power transmission unit disconnects device |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310156198.8A Active CN103573852B (en) | 2012-08-02 | 2013-03-15 | Dual Piston for power transmission unit disconnects device |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US9695884B2 (en) |
| EP (1) | EP2852770B1 (en) |
| CN (2) | CN203384246U (en) |
| WO (1) | WO2014021945A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103573852A (en) * | 2012-08-02 | 2014-02-12 | 伊顿公司 | Dual piston disconnect for power transfer unit |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014127097A1 (en) * | 2013-02-13 | 2014-08-21 | Parker-Hannifin Corporation | Combined power take-off and synchronizer assembly |
| US10174794B2 (en) * | 2016-07-28 | 2019-01-08 | GM Global Technology Operations LLC | Power take-off assembly having a multiple stage clutch |
| BR102017017499A2 (en) | 2016-08-15 | 2018-03-20 | Dana Heavy Vehicle Systems Group, Llc | WHEEL SPEED SENSOR SYSTEM AND METHOD FOR DETERMINING ROTATIONAL SPEED OF A FIRST WHEEL AND A SECOND WHEEL |
| JP6627804B2 (en) * | 2017-02-26 | 2020-01-08 | トヨタ自動車株式会社 | Power transmission device for vehicles |
| US10507691B2 (en) | 2017-10-26 | 2019-12-17 | Strange Oval | Multi-piece spool for an automobile axle assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2518825A (en) | 1946-06-27 | 1950-08-15 | Howard W Simpson | Transmission |
| US2543252A (en) | 1947-04-30 | 1951-02-27 | Snow Nabstedt Gear Corp | Clutch mechanism |
| AT375881B (en) * | 1980-11-26 | 1984-09-25 | Steyr Daimler Puch Ag | DRIVES FOR MOTOR VEHICLES |
| JPH10122344A (en) | 1996-10-23 | 1998-05-15 | Aisin Aw Co Ltd | Control device for vehicular automatic transmission |
| JP4621360B2 (en) * | 1999-05-11 | 2011-01-26 | シーメンス アクチエンゲゼルシヤフト | Electrohydraulic control device for a vehicle, preferably an automobile transmission |
| US6688446B2 (en) | 2001-03-27 | 2004-02-10 | New Venture Gear, Inc. | Rear drive module for all-wheel drive vehicle |
| US7036825B2 (en) * | 2003-08-26 | 2006-05-02 | Delphi Technologies, Inc. | Integrally molded lateral compression seal |
| JP2006029441A (en) | 2004-07-15 | 2006-02-02 | Nissan Motor Co Ltd | Position detecting device of shift fork |
| ATE448421T1 (en) | 2004-08-26 | 2009-11-15 | Hoerbiger & Co | FLUID CLUTCH, ESPECIALLY DOUBLE CLUTCH |
| JP4877905B2 (en) * | 2005-08-03 | 2012-02-15 | 日産自動車株式会社 | Shift position detector for automatic manual transmission |
| SE531602C2 (en) * | 2007-10-12 | 2009-06-02 | Scania Cv Abp | Coupling device and pneumatic system |
| FR2928431B1 (en) * | 2008-03-06 | 2010-09-03 | Peugeot Citroen Automobiles Sa | INTEGRATED HYDRAULICALLY CONTROLLED SYNCHRONIZATION DEVICE FOR A GEARBOX OF A MOTOR VEHICLE |
| DE112009001519A5 (en) * | 2008-07-14 | 2011-04-07 | Schaeffler Technologies Gmbh & Co. Kg | Double coupling |
| US8042642B2 (en) | 2008-08-14 | 2011-10-25 | American Axle & Manufacturing, Inc. | Motor vehicle with disconnectable all-wheel drive system |
| US8721493B2 (en) | 2010-04-07 | 2014-05-13 | GKN Driveline Newton, LLC | Drive train for a motor vehicle |
| CN203384246U (en) * | 2012-08-02 | 2014-01-08 | 伊顿公司 | Double-piston disconnecting device for power transmission unit, and corresponding clutch unit |
-
2013
- 2013-03-15 CN CN201320229055.0U patent/CN203384246U/en not_active Expired - Lifetime
- 2013-03-15 CN CN201310156198.8A patent/CN103573852B/en active Active
- 2013-03-15 EP EP13714411.9A patent/EP2852770B1/en active Active
- 2013-03-15 WO PCT/US2013/031987 patent/WO2014021945A1/en active Application Filing
- 2013-03-15 US US14/408,098 patent/US9695884B2/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103573852A (en) * | 2012-08-02 | 2014-02-12 | 伊顿公司 | Dual piston disconnect for power transfer unit |
| CN103573852B (en) * | 2012-08-02 | 2017-03-01 | 伊顿公司 | Dual Piston for power transmission unit disconnects device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103573852B (en) | 2017-03-01 |
| US20150167750A1 (en) | 2015-06-18 |
| EP2852770B1 (en) | 2019-10-16 |
| CN103573852A (en) | 2014-02-12 |
| US9695884B2 (en) | 2017-07-04 |
| WO2014021945A1 (en) | 2014-02-06 |
| EP2852770A1 (en) | 2015-04-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190701 Address after: Dublin, Ireland Patentee after: Eaton Intelligent Power Co.,Ltd. Address before: Ohio, USA Patentee before: Eaton Corp. |
|
| TR01 | Transfer of patent right | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140108 |
|
| CX01 | Expiry of patent term |